KR20060016655A - A 6-speed power train of an automatic transmission - Google Patents

Abstract

The present invention constitutes a driven shaft side by side with respect to the input shaft from which the rotational force is input from the engine, and on each axis to form a simple planetary gear set and a complex planetary gear set, respectively, to reduce the length (length) in the longitudinal direction of the transmission, It is to provide a six-speed power train of an automatic transmission for a vehicle that can improve the power transmission efficiency, and at the same time implement a sixth speed forward and one reverse speed.

Automatic transmission. clutch. Planetary gear set, input shaft, driven shaft

Description

A 6-SPEED POWER TRAIN OF AN AUTOMATIC TRANSMISSION}

1 is a schematic diagram of a power train according to an embodiment of the present invention;

2 is a table of the operating elements of the power train applied to all embodiments of the present invention,

3 and 4 is a sixth forward and reverse shift diagram of the power train according to an embodiment of the present invention,

5 is a schematic diagram of a conventional power train,

6 is an operating element table of the power train according to FIG. 5, and

7 is a forward speed 1 to 6 speed and a reverse shift diagram of a conventional power train.

The present invention relates to a six-speed power train of an automatic transmission, and more particularly, to configure a driven shaft side by side with respect to the input shaft input rotational force from the engine, each of which comprises a simple planetary gear set and a complex planetary gear set The present invention relates to a six-speed power train of an automatic transmission for a vehicle that can reduce the size of the longitudinal direction (full length) and improve the power transmission efficiency, and at the same time realize the sixth speed forward and one reverse speed.

For example, the multi-speed gear mechanism of an automatic transmission is composed of a combination of a plurality of planetary gear sets, and a power train in which the plurality of planet gear sets is combined, when a rotational power is input from a torque converter that converts and transmits engine torque, is transmitted. It performs the function of transmitting to the output side by shifting to multiple stages.

Since the power train of the automatic transmission has more shift stages, it is advantageous in terms of power performance and fuel consumption rate, and thus, a power train capable of implementing more shift stages is required.

Also, even if the same number of gear stages are implemented, durability, power transmission efficiency, size and weight vary greatly depending on the combination method of the planetary gear set. Therefore, the power train can be more robust and compact while minimizing power loss. Efforts for development are ongoing.

Thus, in developing a power train using a planetary gear set, rather than developing a new planetary gear set, a conventional single pinion planetary gear set, a double pinion planetary gear set, or a single and double pinion planetary gear How to combine a set of combination type planetary gear set and the accompanying clutches, brakes and one-way clutches in any position to achieve the desired speed and the gear ratio without any possible power loss Various studies are aimed at improving the performance.

In particular, in the case of a manual transmission, the driver has to shift frequently if there are too many shift stages. However, in the case of an automatic transmission, the transmission control unit automatically controls the operation of the power train according to the driving state. Therefore, it is very important to develop a power train that can realize more shift stages.

In order to cope with this trend, various researches on 4 speed and 5 speed power trains are being conducted, and in recent years, power trains of automatic transmissions capable of implementing 6 speed forward and 1 speed reverse gears have been provided.

As an example, as shown in FIG. 5, one single pinion planetary gear set (SPG) in front and one lavender type planetary gear set (LPG) in the rear are combined, but the single pinion planetary gear set (SPG) is combined. The first sun gear S1 is fixed to the transmission case 1, and the second (3) ring gear R2 (R3) of the planetary gear set LPG is mounted with an output gear OUT. Will work.

The first ring gear R1 of the single pinion planetary gear set SPG is directly connected to the input shaft 3, and connects the second and third planetary gears P2 and P3 of the rib planetary gear set LPG. The third planet carrier PC3 is variably connected to the input shaft 3 via the second clutch C2.

Further, the first planet carrier PC1 connecting the first planetary gear P1 of the single pinion planetary gear set SPG may have a first clutch between the third sun gear S3 of the rib planetary gear set LPG. They are variably connected to each other via (C1), which in turn are variably connected to each other via a third clutch (C3) between the second sun gear (S2).

In addition, the second sun gear S2 is connected to the transmission case 1 via the first brake B1 and connects the second and third planetary gears P2 and P3 of the rib planetary gear set LPG. The third planet carrier PC3 to be connected is connected to the transmission case 1 via a second brake B2 arranged in parallel with the transmission case 1 and a one-way clutch OWC.

As shown in FIGS. 6 and 7, the power train operates the first clutch C1 and the one-way clutch OWC at the forward shift stage to implement the first speed stage 1ST, and the first clutch C1 and the first clutch C1. The first brake B1 operates to implement the second speed stage 2ND, and the first clutch C1 and the third clutch C3 operate to implement the third speed stage 3RD.

The first clutch C1 and the second clutch C2 operate to implement the fourth speed stage 4TH, and the second and third clutch C2 and C3 operate to implement the fifth speed stage 5TH. The second clutch C2 and the first brake B1 operate to implement the sixth speed 6TH.

In the reverse shift stage, the third clutch C3 and the second brake B2 operate to implement the reverse first speed REW, and thus, the overall shift speed of the sixth forward speed and the first reverse speed is realized.

However, as described above, the six-speed power train of the conventional automatic transmission has a length (length) of the transmission length as the single pinion planetary gear set and the rib planetary gear set are disposed adjacent to each other on an input shaft through which rotational force is input from the engine. It is lengthened and the mountability in the engine room is reduced, and the disadvantages of increasing the power transmission efficiency due to the limitation of the layout by forming a planetary gear set on the same axis.

Accordingly, the present invention has been invented to solve the problems of the prior art, the object of the present invention is to configure the driven shaft side by side with respect to the input shaft to which the rotational force is input from the engine, and a simple planetary gear set on each axis The automatic transmission for vehicles is configured to reduce the size of the transmission (length) in the longitudinal direction of the transmission, improve the power transmission efficiency, and to realize the transmission speeds of 6 forward speed and 1 reverse speed, respectively. To provide a six-speed power train.

The six-speed power train of the automatic transmission of the present invention for achieving the above object,

An input shaft to which rotational force of the engine is input; A driven shaft spaced apart from the input shaft at a predetermined interval and arranged in parallel; On the input shaft, the first sun gear is fixed to the transmission case with a constantly fixed element, the first planet carrier is combined with a deceleration element, and the first ring gear is directly connected to the input shaft to be combined as an always input element to drive three operating elements. A simple planetary gearset to implement; On the driven shaft, a ring gear and a planetary carrier are respectively shared, and the shared ring gear is combined as an output element, and the shared planetary carrier is variably connected to the driven shaft via a third clutch and simultaneously connected to the transmission case. The first brake and the one-way clutch arranged in parallel are variably connected to the transmission case, and the non-shared second and third sun gears are combined to operate as variable input elements, respectively, to implement four operating elements, and the input shaft A composite planetary gear set that receives rotational force from three input paths; A first mediated gear set configured between the input shaft and the driven shaft to transmit rotational force of the input shaft to the driven shaft at the same speed; A first power transmission member on the input shaft and the first power transmission member on the input shaft to decelerate the rotational force of the input shaft through the first planetary carrier of the simple planetary gear set and to transmit to the third sun gear of the compound planetary gear set on the driven shaft by the operation of the first clutch; A second mediated gear set disposed adjacent to the first mediated gear set by a second power transmission member on the driven shaft; The rotational force of the input shaft is decelerated through the first planetary carrier of the simple planetary gear set and transmitted to the second sun gear of the compound planetary gear set on the driven shaft by the operation of the second clutch, and the second brake is operated by the operation of the second brake. A third mediated gear disposed adjacent to the second mediated gear set by a third power transmission member on the first power transmission member and a fourth power transmission member on the second power transmission member to combine the two-wire gear into a variable fixed element. Including the set, it is characterized by implementing the speed shift stage of 6 forward speed and 1 reverse speed.

Hereinafter, with reference to the accompanying drawings, preferred embodiments of the present invention will be described in more detail.

1 is a schematic diagram of a power train according to an exemplary embodiment of the present invention, wherein the power train according to the exemplary embodiment of the present invention is connected to an engine output side through a torque converter (not shown) so that an input shaft 3 into which the rotational force of the engine is input is provided. It is provided.

In addition, the driven shaft 5 is provided parallel to the input shaft 3 spaced apart by a predetermined interval.

On the input shaft 3, a single pinion planetary gear set SPG composed of a first sun gear S1, a first planetary gear P1, and a first ring gear R1 is provided, and the single pinion planetary gear set SPG is provided. ) Is the first sun gear (S1) is always fixed to the transmission case (1) as a fixed element, the first ring gear (R1) connected to the first sun gear (S1) through the first planetary gear (P1) is upper. Directly connected to the input shaft (3) is always combined as an input element.

Here, the single pinion planetary gear set (SPG) is the first sun gear (S1), the first ring gear (R1), the first sun gear (S1) and the first ring gear (R1) is meshed between the first ring gear (R1). It includes three actuating elements including a first planetary carrier PC1 for rotatably supporting one planetary gear P1.

And on the driven shaft (5), the second sun gear (S2), the third sun gear (S3), and two planetary gears (P2, P3) share, and at the same time a third ring gear (R3) share the planetary planet Gear set LPG is provided in combination.

Herein, the planetary planetary gear set LPG includes two sets of planetary gears P2 and P3 meshed between the second sun gear S2 and the third sun gear S3 and the third ring gear R3. And second and third planetary carriers PC2 and PC3 rotatably supported.

The shared planetary gear set LPG includes the shared third ring gear R3 as an output element, and the shared third planet carrier PC3 is connected to the driven shaft through a third clutch C3. 5) and the second planetary carrier PC2 shared at the same time, the first brake (B1) and the one-way clutch (OWC) disposed in parallel to the transmission case (1) to the transmission case (1) Variable connection.

In addition, the second and third sun gears S2 and S3, which are not shared by the planetary gear set LPG, are combined to operate as a variable input element, and are implemented as four operating elements, and a rotational force from the input shaft 3. It is configured to receive input through three input paths.

And between the input shaft (3) and the driven shaft (5) a first mediated gear set (MS1) is configured to transmit the rotational force of the input shaft 3 to the driven shaft (5) at the same time, the first parameter The gear set MS1 is equipped with a first driving medium gear M1 at one end on the input shaft 3, and at the one end on the driven shaft 5 corresponding to the first driving medium gear M1. The first driven intermediate gear (M2) to be engaged is configured.

Here, the first driving medium gear (M1) and the first driven medium gear (M2) is preferably made of a helical gear having a gear ratio of one to one (1: 1).

Then, the rotational force of the input shaft 3 is decelerated through the first planetary carrier PC1 of the single-pinion planetary gear set SPG to operate the first clutch C1 so that the rib planetary on the driven shaft 5 is operated. First mediation by the first power transmission member 7 on the input shaft 3 and the second power transmission member 9 on the driven shaft 5 to transmit to the third sun gear S3 of the gear set LPG. The second mediated gear set MS2 is disposed adjacent to the gear set MS1.

That is, the second intermediate gear set MS2 has a second driving intermediate gear M3 disposed on one side of the input shaft 3 so that the second intermediate gear set MS2 is disposed on the first planetary carrier PC1 of the single pinion planetary gear set SPG. It is connected via the clutch C1.

At this time, the second drive medium gear (M3) is connected to the first planetary carrier (PC1) through a first power transmission member (7), the first power transmission member (7) is the input shaft (3) It is preferably made of a hollow shaft surrounding the bed.

In addition, the second intermediate gear set MS2 has a second driven intermediate gear M4 disposed on one side of the driven shaft 5 so as to be engaged with the second driving intermediate gear M3. It is directly connected to the third sun gear S3 of the gear set LPG through the second power transmission member 9.

At this time, the second power transmission member 9 is preferably made of a hollow shaft surrounding it on the driven shaft (5).

Here, the second driving medium gear (M3) and the second driven medium gear (M4) is preferably made of a helical gear having a gear ratio of one to one (1: 1), respectively.

Then, the rotational force of the input shaft 3 is decelerated through the first planetary carrier PC1 of the single-pinion planetary gear set SPG to operate the second clutch C2 so that the planetary gear on the driven shaft 5 is operated. The outer side on the first power transmission member 7 so as to be transmitted to the second sun gear S2 of the set LPG or the second sun gear S2 is combined into the variable fixing element by the operation of the second brake B2. A third power transmission member 11 disposed in the second transmission gear set MS2 adjacent to the second mediated gear set MS2 by a fourth power transmission member 13 disposed on the outside on the second power transmission member 9; The intermediate gear set MS3 is disposed.

That is, the third intermediate gear set MS3 has a third driving medium gear M5 disposed on one side of the input shaft 3 so that the third intermediate gear set MS3 is disposed on the first planetary carrier PC1 of the single pinion planetary gear set SPG. It is connected via two clutches C2.

At this time, the third drive medium gear (M5) is connected to the first planetary carrier (PC1) through a third power transmission member 11, the third power transmission member 11 is the input shaft (3) It is preferably made of a hollow shaft surrounding the bed.

In addition, the third driving medium gear M5 is variably connected with the transmission case 1 through the second brake B2, which is also connected by the third power transmission member 11.

In addition, the third intermediate gear set MS3 has a third driven intermediate gear M6 disposed on one side of the driven shaft 5 such that the third intermediate gear set MS3 is engaged with the third driving medium gear M5. It is directly connected to the second sun gear S2 of the gear set LPG through the fourth power transmission member 13.

At this time, the fourth power transmission member 13 is preferably made of a hollow shaft surrounding it on the driven shaft (5).

Here, the third driving medium gear (M5) and the third driven medium gear (M6) is preferably made of a helical gear having a gear ratio of one to one (1: 1).

Therefore, according to the above configuration, the single pinion planetary gear set SPG is combined with the first sun gear S1 directly to the transmission case 1 into the first operating element which is the fixed element, and the first planetary carrier ( PC1) is combined with a second operating element which is a deceleration element, and the first ring gear R1 is combined with a third operating element which is always an input element in direct connection with the input shaft 3 to implement three operating elements.

Also, the planetary planetary gear set LPG shares the third ring gear R3 and the second and third planet carriers PC2 and PC3, respectively, and the shared third ring gear R3 is an output element. Combined into six operating elements, the shared second planetary carrier PC2 is variably connected via a first brake B1 and a one-way clutch OWC disposed in parallel to the transmission case 1 and shared therewith. The third planet carrier PC3 is variably connected to the driven shaft 5 via the third clutch C2 and is combined into a fifth operating element which is a variable fixed element and a variable input element.

In addition, the non-shared third sun gear S3 inputs the decelerated rotational force of the input shaft 3 from the first planet carrier PC2 through the second intermediate gear set MS2 according to the operation of the first clutch C1. The second sun gear S2, which is combined with the seventh operating element, which is a variable input element that is received, and which is not shared, is connected to the first planet carrier PC2 through the third mediated gear set MS3 according to the operation of the second clutch C2. Four operating elements are realized by combining the reduced rotational force of the input shaft 3 from the fourth operating element, which is a variable input element.

Here, the first and second clutches C1 and C2 and the second brake B2 are disposed on the single pinion planetary gear set SPG configured on the input shaft 3.

In addition, the first brake B1, the one-way clutch OWC, and the third clutch C3 disposed in parallel to the transmission case 1 may include a planetary gear set configured on the driven shaft 5. LPG) side.

The power train having these seven operating elements is output through the third ring gear R3 shared by the planetary gear set LPG, as shown in the operating element table shown in FIG. The first speed is achieved by the operation of the first clutch C1 and the one-way clutch OWC, and the second speed is achieved by the operation of the second brake B2 in the state of the first speed. At the second speed, the second brake C2 is released while the second brake B2 is released. In the fourth speed, the second clutch C2 is released at the third speed. While being made by the operation of the third clutch (C3), in the fifth speed stage in the state of the fourth speed, the first clutch (C1) is released by the operation of the second clutch (C2), the sixth speed In the state of the fifth speed, the second clutch (C2) is released by the operation of the second brake (B2) In the reverse shift stage, the sixth forward speed and the reverse speed are realized by the operation of the second clutch C2 and the first brake B1.

In this way, the combined power train is transmitted from the single-pinion planetary gear set (SPG) to the rib planetary gear set (LPG) through the three input paths, the first input path The rotational force of the input shaft (3) is variably connected to the driven shaft (5) through the first driving medium gear (M1) and the first driven medium gear (M2) of the first intermediate gear set (MS1) The third clutch C3, which is input at the same speed to the three planetary carriers PC3 and variably connects the shared third planetary carrier PC3 of the rib planetary gearset LPG to the driven shaft 5, is operated. By the input of the input shaft 3 is made to receive at the same speed.

The second input path has a second driving medium of the second mediated gear set MS2 while the rotational force of the input shaft 3 is decelerated by the first planet carrier PC1 of the single pinion planetary gear set SPG. The first planetary gear of the single pinion planetary gear set SPG is inputted to the third sun gear S3 of the planetary gear set LPG through the gear M3 and the second driven intermediate gear M4. The first clutch C1 variably connects the carrier PC1 to the second mediated gear set MS2.

The third input path is also driven by the third drive gear set MS3 with the rotational force of the input shaft 3 being decelerated by the first planet carrier PC1 of the single pinion planetary gear set SPG. The first gear of the single pinion planetary gear set SPG is inputted to the second sun gear S2 of the planetary gear set LPG through the intermediate gear M5 and the third driven intermediate gear M6. The operation of the second clutch C2 variably connects the planet carrier PC1 to the third mediated gear set MS3.

The shifting process of the power train according to the embodiment of the present invention described above will be described in more detail with reference to FIGS. 3 and 4.

First, as described above, each actuating element is disposed in each actuating element for each node, as shown in the first to sixth forward and backward shift diagrams of the power train according to the present invention of FIGS. 3 and 4. N1) is a first sun gear S1, which is a first operating element, a second node N2, and a third node N3, a first planetary carrier PC1 and a first ring gear, which are second and third operating elements. R1), the fourth node (N4) is a second sun gear (S2) that is the fourth operating element, the fifth node (N5) is a second, third planetary carrier (PC2, PC3) that is a fifth operating element Is set.

In addition, the sixth node N6 has a third ring gear R3 which is a sixth operating element, and the seventh node N7 has a third sun gear S3 which is a seventh operating element.

Accordingly, the third node N3, which is the first ring gear R1 of the single pinion planetary gear set SPG on the input shaft 3, is operated with the first clutch C1 and the one-way clutch OWC operating. When an input is made through the first planetary carrier PC1, the input decelerated by the planetary gear set on the driven shaft 5 on the driven shaft 5 through the second driving medium gear M3 and the second driven medium gear M4. It is input to the seventh node N7 which is the third sun gear S3 of LPG.

At this time, the second planetary carrier PC2 of the planetary planetary gear set LPG is operated as a fixed element, and forms the speed line L1 as shown in the first velocity diagram of FIG. The output is made as much as D1 through the sixth node N6, that is, the third ring gear R3 to be shared.

In the second forward speed, in the state of the first speed, the second brake B2 is operated.

In this case, when an input is made through the third node N3 which is the first ring gear R1 of the single pinion planetary gear set SPG on the input shaft 3, the speed is reduced by the first planet carrier PC1. The input is via the second driving medium gear M3 and the second driven medium gear M4 to the seventh node N7, which is the third sun gear S3 of the rib planetary gear set LPG on the driven shaft 5. Is entered.

In addition, the operation of the second brake (B2) is the second sun gear (LPG) of the planetary gear set LPG on the driven shaft (5) through the third driving medium gear (M5) and the third driven medium gear (M6) By fixing S2) to make the fourth node N4 act as a fixing element, the speed line L2 is formed as shown in the second speed diagram of FIG. 3, and through the sixth node N6 as an output element, D2 is formed. As the output is made, the shifting speed of the 2nd forward is made.

At the third forward speed, in the state of the second speed, the operation of the second brake B2 is released, and the second clutch C2 is operated.

Accordingly, the input is made through the third node N3, which is the first ring gear R1 of the single pinion planetary gear set SPG on the input shaft 3, and is decelerated by the first planet carrier PC1. The input is via the second driving medium gear M3 and the second driven medium gear M4 to the seventh node N7, which is the third sun gear S3 of the rib planetary gear set LPG on the driven shaft 5. Is entered.

At this time, the operation of the second clutch C2 is input through the third node N3 which is the first ring gear R1 of the single pinion planetary gear set SPG on the input shaft 3. Through the gear M5 and the third driven intermediate gear M6, the second planetary gear set LPG of the rib planetary gear set LPG on the driven shaft 5 is transmitted as it is to the fourth node N4. The same input as node N7 is made.

Accordingly, as shown in the third speed diagram of FIG. 3, the speed line L3 is formed, and the output is made as much as D3 through the sixth node N6, which is an output element, and the third speed is shifted.

At the fourth forward speed, the operation of the second clutch C2 is released in the state of the third speed, and the third clutch C3 is controlled to operate.

Then, while the input is made through the third node N3, which is the first ring gear R1 of the single pinion planetary gear set SPG on the input shaft 3, the input reduced by the first planet carrier PC1. The second drive medium (M3) and the second driven medium (M4) are input to the seventh node (N7), which is the third sun gear (S3) of the rib planetary gear set (LPG) on the driven shaft (5). do.

At the same time, with the operation of the third clutch C3, the third planet carrier PC3 of the shared planetary gear set LPG is inputted from the input shaft 3 to the first driving intermediate gear M1. And the driven shaft 5 transmitted at the same speed through the first driven intermediate gear M2 to receive the input of the input shaft 3 as it is.

Accordingly, the reduced planetary gear set LPG is transmitted to the seventh node N7, and the input of the same speed as the input shaft is transmitted to the fifth node N5. The speed line L4 is formed as shown in FIG. 6, and the output is made as much as D4 through the sixth node N6, which is an output element.

In the fifth forward speed, the first clutch C1 is released in the fourth speed state, and the second clutch C2 is operated.

Then, in operation of the third clutch C3, the shared third planetary carrier PC3 of the lavender planetary gear set LPG has an input from the input shaft 3, and the first drive medium gear M1. And a driven shaft 5 which is transmitted at the same speed through the first driven intermediate gear M2 to receive the input of the input shaft 3 as it is.

At the same time, the operation of the second clutch C2 is such that the input through the third node N3, which is the first ring gear R1 of the single pinion planetary gear set SPG on the input shaft 3, is controlled by the third driving medium. The gear M5 and the third driven intermediate gear M6 are transmitted to the second sun gear S2 of the rib planetary gear set LPG on the driven shaft 5 as it is.

Accordingly, the reduced planetary gear set LPG is transmitted to the fourth node N4, and the fifth node N5 is transmitted to the input shaft at the same speed as the input shaft. The speed line L5 is formed as shown in FIG. 5 and the output is made as much as D5 through the sixth node N6, which is an output element.

At the sixth forward speed, the operation of the second clutch C5 is released in the state of the fifth speed, and the second brake B2 is controlled to operate.

Then, in operation of the third clutch C3, the shared third planetary carrier PC3 of the lavender planetary gear set LPG has an input from the input shaft 3, and the first drive medium gear M1. And it is connected to the driven shaft (5) transmitted at the same speed through the first driven intermediate gear (M2) and receives the input of the input shaft (3) as it is.

At the same time, the second sun gear of the rib planetary gear set LPG on the driven shaft 5 through the third driving medium gear M5 and the third driven medium gear M6 by the operation of the second brake B2. By fixing (S2) to act as a fixing element to the fourth node (N4), to form a speed line (L6) as shown in the sixth speed diagram of Figure 4, the sixth node (N6) as an output element) As the output is made by D6, the 6th forward speed is made.

Finally, in the reverse shift stage, the second clutch C2 and the first brake B1 are operated and controlled.

Then, the input through the third node N3, which is the first ring gear R1 of the single pinion planetary gear set SPG on the input shaft 3, is operated by the operation of the second clutch C2. It is transmitted as it is to the second sun gear S2 of the rib planetary gear set LPG on the driven shaft 5 through M5 and the third driven intermediate gear M6.

In this state, when the first brake B1 is operated, the shared second planetary carrier PC2 of the lavender planetary gearset LPG is operated as a fixed element.

Accordingly, the L-bino planetary gear set LPG forms the speed line LR as shown in the reverse speed diagram of FIG. 4, and the reverse shift is performed as much as R through the sixth node N6, which is an output element. This will be done

While one embodiment of the power train of the present invention has been described above, the present invention is not limited to the above embodiment, and those of ordinary skill in the art to which the present invention pertains easily from the embodiment of the present invention. Invention includes all modifications to the extent deemed equivalent.

As described above, the power train of the present invention constitutes a driven shaft side by side with respect to an input shaft into which rotational force is input from the engine, and on each axis, a simple planetary gear set and a composite planetary gear set are respectively configured to provide a longitudinal direction of the transmission. By reducing the size (full length), there is an effect of improving the mountability in the engine compartment.

In addition, by forming a planetary gear set through two rotation shafts consisting of an input shaft and a driven shaft, the fluidity of the layout is increased, which is advantageous in improving power transmission efficiency.

Claims (35)

In the six-speed power train of the automatic transmission, An input shaft to which rotational force of the engine is input; A driven shaft spaced apart from the input shaft at a predetermined interval and arranged in parallel; A simple planetary gear set configured on the input shaft; A composite planetary gear set configured on the driven shaft; A first mediated gear set configured between the input shaft and the driven shaft to transmit rotational force of the input shaft to the driven shaft at the same speed; Disposed adjacent to the first mediated gear set on the input shaft and driven shaft so as to reduce the rotational force of the input shaft through one actuating element of the simple planetary gear set and transmit it to one actuating element of the compound planetary gear set on the driven shaft. A second mediated gear set; Adjacent to the second intermediate gear set on the input shaft and driven shaft to decelerate the rotational force of the input shaft through one actuating element of the simple planetary gear set and transmit it to the other actuating element of the compound planetary gear set on the driven shaft. The sixth speed train of the automatic transmission, characterized in that for implementing the sixth speed forward and the first speed reverse gear stage, including; The method of claim 1, wherein the simple planetary gear set The first sun gear is fixed to the transmission case to operate as a fixed element at all times, and the first planetary carrier is connected to the second mediation gear set with the first clutch as a deceleration element, and the second clutch and the transmission case 6 of the automatic transmission characterized in that it is connected to the third mediation gear set via a second brake connected, and the first ring gear is connected to the input shaft directly to form three operating elements in combination with the input shaft at all times. Genus power train. The method of claim 1, wherein the simple planetary gear set A six-speed power train for an automatic transmission, characterized by a single pinion planetary gearset. The method of claim 1, wherein the composite planetary gear set A ring gear and a planet carrier are respectively shared, and the shared ring gear is combined as an output element, and the shared planet carrier is variably connected to the driven shaft via a third clutch and is arranged in parallel to the transmission case. The second and third sun gears, which are variably connected to the transmission case through one brake and a one-way clutch, are directly connected to the second and third mediated gear sets, respectively, so as to reduce the rotational force from the simple planetary gear set. 6-speed power train of an automatic transmission, characterized in that the four transmission elements in combination to receive the transmission. The method of claim 1, wherein the composite planetary gear set A six-speed power train of an automatic transmission, characterized in that it comprises a ring planetary gear set that shares the ring gear and the planet carrier. The method of claim 1, wherein the first mediated gear set A first driving intermediate gear mounted on one side of the input shaft; And a first driven intermediate gear mounted on one side of the driven shaft and meshed with the first driving intermediate gear. The method of claim 6, wherein the first drive medium gear and the first driven medium gear A six-speed power train of an automatic transmission, characterized in that each gear ratio consists of a helical gear consisting of one-to-one (1: 1). The method of claim 1, wherein the second mediated gear set A second drive medium gear disposed on one side of the input shaft and connected by a first power transmission member to be connected to a first planet carrier of the simple planetary gear set through a first clutch; A second driven intermediate gear disposed on one side of the driven shaft and directly connected to the third sun gear of the composite planetary gear set by a second power transmission member and meshed with the second driving intermediate gear; 6-speed power train with automatic transmission. The method according to claim 8, wherein the first power transmission member The six-speed power train of the automatic transmission, characterized in that consisting of a hollow shaft surrounding it on the input shaft. The method of claim 8, wherein the second power transmission member The six-speed power train of the automatic transmission, characterized in that consisting of a hollow shaft surrounding it on the driven shaft. The method of claim 8, wherein the second drive medium gear and the second driven medium gear A six-speed power train of an automatic transmission, characterized in that each gear ratio consists of a helical gear consisting of one-to-one (1: 1). The method of claim 1, wherein the third mediated gear set A third drive intermediate gear disposed on one side of the input shaft and connected by a third power transmission member to be connected to a first planet carrier of the simple planetary gear set through a second clutch; A third driven intermediate gear disposed on one side of the driven shaft and directly connected to the second sun gear of the composite planetary gear set by a fourth power transmission member and engaged with the third driving intermediate gear; 6-speed power train with automatic transmission. The method of claim 12, wherein the third power transmission member The six-speed power train of the automatic transmission, characterized in that consisting of a hollow shaft surrounding it on the input shaft. The method of claim 12, wherein the fourth power transmission member The six-speed power train of the automatic transmission, characterized in that consisting of a hollow shaft surrounding it on the driven shaft. The method of claim 12, wherein the third drive medium gear and the third driven medium gear A six-speed power train of an automatic transmission, characterized in that each gear ratio consists of a helical gear consisting of one-to-one (1: 1). In the six-speed power train of the automatic transmission, An input shaft to which rotational force of the engine is input; A driven shaft spaced apart from the input shaft at a predetermined interval and arranged in parallel; On the input shaft, the first sun gear is fixed to the transmission case with a constantly fixed element, the first planet carrier is combined with a deceleration element, and the first ring gear is directly connected to the input shaft to be combined as an always input element to drive three operating elements. A simple planetary gearset to implement; On the driven shaft, a ring gear and a planetary carrier are respectively shared, and the shared ring gear is combined as an output element, and the shared planetary carrier is variably connected to the driven shaft via a third clutch and simultaneously connected to the transmission case. The first brake and the one-way clutch arranged in parallel are variably connected to the transmission case, and the non-shared second and third sun gears are combined to operate as variable input elements, respectively, to implement four operating elements, and the input shaft A composite planetary gear set that receives rotational force from three input paths; A first mediated gear set configured between the input shaft and the driven shaft to transmit rotational force of the input shaft to the driven shaft at the same speed; A first power transmission member on the input shaft and the first power transmission member on the input shaft to decelerate the rotational force of the input shaft through the first planetary carrier of the simple planetary gear set and to transmit to the third sun gear of the compound planetary gear set on the driven shaft by the operation of the first clutch; A second mediated gear set disposed adjacent to the first mediated gear set by a second power transmission member on the driven shaft; The rotational force of the input shaft is decelerated through the first planetary carrier of the simple planetary gear set and transmitted to the second sun gear of the compound planetary gear set on the driven shaft by the operation of the second clutch, and the second brake is operated by the operation of the second brake. A third mediated gear disposed adjacent to the second mediated gear set by a third power transmission member on the first power transmission member and a fourth power transmission member on the second power transmission member to combine the two-wire gear into a variable fixed element. 6-speed power train of an automatic transmission, including a; 6-speed forward and 1-speed forward gear stage including a set. The method of claim 16, wherein the simple planetary gear set A six-speed power train for an automatic transmission, characterized by a single pinion planetary gearset. The method of claim 16, wherein the planetary gear set A six-speed power train of an automatic transmission, characterized in that it comprises a ring planetary gear set that shares the ring gear and the planet carrier. The method of claim 16, wherein the first mediated gear set A first driving intermediate gear mounted on one side of the input shaft; And a first driven intermediate gear mounted on one side of the driven shaft and meshed with the first driving intermediate gear. 20. The method of claim 19, wherein the first drive medium gear and the first driven medium gear 6-speed power train of an automatic transmission, characterized in that each consisting of a helical gear. The method of claim 16, wherein the second mediated gear set A second drive medium gear disposed on one side of the input shaft and connected by a first power transmission member to be connected to a first planet carrier of the simple planetary gear set through a first clutch; A second driven intermediate gear disposed on one side of the driven shaft and directly connected to the third sun gear of the composite planetary gear set by a second power transmission member and meshed with the second driving intermediate gear; 6-speed power train with automatic transmission. The method of claim 21, wherein the first power transmission member The six-speed power train of the automatic transmission, characterized in that consisting of a hollow shaft surrounding it on the input shaft. The method of claim 21, wherein the second power transmission member The six-speed power train of the automatic transmission, characterized in that consisting of a hollow shaft surrounding it on the driven shaft. The method of claim 21, wherein the second drive medium gear and the second driven medium gear A six-speed power train of an automatic transmission, characterized in that each gear ratio consists of a helical gear consisting of one-to-one (1: 1). The method of claim 16, wherein the third mediated gear set A third drive intermediate gear disposed on one side of the input shaft and connected by a third power transmission member to be connected to a first planet carrier of the simple planetary gear set through a second clutch; A third driven intermediate gear disposed on one side of the driven shaft and directly connected to the second sun gear of the composite planetary gear set by a fourth power transmission member and engaged with the third driving intermediate gear; 6-speed power train with automatic transmission. The method of claim 25, wherein the third power transmission member The six-speed power train of the automatic transmission, characterized in that consisting of a hollow shaft surrounding it on the input shaft. The method of claim 25, wherein the fourth power transmission member The six-speed power train of the automatic transmission, characterized in that consisting of a hollow shaft surrounding it on the driven shaft. The method of claim 25, wherein the third drive medium gear and the third driven medium gear A six-speed power train of an automatic transmission, characterized in that each gear ratio consists of a helical gear consisting of one-to-one (1: 1). The method of claim 16, wherein the input path through which the power of the input shaft is transmitted to the composite planetary gear set A first input path through which the rotational force of the input shaft is input at the same speed to a shared planetary carrier variably connected to the driven shaft through the first mediated gear set; A second input path in which the rotational force of the input shaft is decelerated by the first planetary carrier of the simple planetary gear set and is inputted to the third sun gear of the composite planetary gear set through the second intermediate gear set as a deceleration; And a third input path in which the rotational force of the input shaft is decelerated by the first planetary carrier of the simple planetary gear set and is decelerated and input to the second sun gear of the composite planetary gear set through the third mediated gear set. 6-speed power train with automatic transmission. 30. The method of claim 29, wherein the first input path And a sixth speed train of the automatic transmission, wherein the third clutch variably connects the shared planetary carrier to the driven shaft. 30. The method of claim 29, wherein the second input path And a sixth speed train of the automatic transmission, wherein the first clutch variably connects the first planetary carrier of the simple planetary gearset to the second mediated gearset. 30. The method of claim 29, wherein the third input path And a second clutch for variably connecting the first planetary carrier of the simple planetary gearset to the third mediated gearset. The method of claim 16, wherein the output of the shared ring gear of the composite planetary gear set It is made by the operation of the first clutch and the one-way clutch in the first speed, in the second speed by the operation of the second brake in the state of the first speed, and in the state of the second speed in the third speed The brake is released by the operation of the second clutch, the fourth speed is in the state of the third speed, the second clutch is released by the operation of the third clutch, the fifth speed is the state of the fourth speed The first clutch is released by the operation of the second clutch, the sixth speed is made by the operation of the second brake while the second clutch is released in the state of the fifth speed, the second clutch in the reverse shift stage And a six-speed power train of the automatic transmission, characterized in that the first brake is operated. The method of claim 16, wherein the first clutch, the second clutch and the second brake And a six-speed power train of the automatic transmission, characterized in that disposed on the side of the simple planetary gear set configured on the input shaft. The method of claim 16, wherein the first brake, the one-way clutch and the third clutch disposed in parallel to the transmission case And a six-speed power train of the automatic transmission, characterized in that disposed on the side of the composite planetary gear set configured on the driven shaft.

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